EP2630366B1 - Ensemble rotor de turbine - Google Patents

Ensemble rotor de turbine Download PDF

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Publication number
EP2630366B1
EP2630366B1 EP11833628.8A EP11833628A EP2630366B1 EP 2630366 B1 EP2630366 B1 EP 2630366B1 EP 11833628 A EP11833628 A EP 11833628A EP 2630366 B1 EP2630366 B1 EP 2630366B1
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EP
European Patent Office
Prior art keywords
blade
blades
rotor assembly
turbine rotor
hub
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Active
Application number
EP11833628.8A
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German (de)
English (en)
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EP2630366A1 (fr
EP2630366A4 (fr
Inventor
Peter John Murdoch
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Wave Power Renewables Ltd
Original Assignee
Wave Power Renewables Ltd
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Priority claimed from AU2010904731A external-priority patent/AU2010904731A0/en
Application filed by Wave Power Renewables Ltd filed Critical Wave Power Renewables Ltd
Publication of EP2630366A1 publication Critical patent/EP2630366A1/fr
Publication of EP2630366A4 publication Critical patent/EP2630366A4/fr
Application granted granted Critical
Publication of EP2630366B1 publication Critical patent/EP2630366B1/fr
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F03—MACHINES OR ENGINES FOR LIQUIDS; WIND, SPRING, OR WEIGHT MOTORS; PRODUCING MECHANICAL POWER OR A REACTIVE PROPULSIVE THRUST, NOT OTHERWISE PROVIDED FOR
    • F03B—MACHINES OR ENGINES FOR LIQUIDS
    • F03B3/00—Machines or engines of reaction type; Parts or details peculiar thereto
    • F03B3/12—Blades; Blade-carrying rotors
    • F03B3/14—Rotors having adjustable blades
    • F03B3/145—Mechanisms for adjusting the blades
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01D—NON-POSITIVE DISPLACEMENT MACHINES OR ENGINES, e.g. STEAM TURBINES
    • F01D5/00—Blades; Blade-carrying members; Heating, heat-insulating, cooling or antivibration means on the blades or the members
    • F01D5/30—Fixing blades to rotors; Blade roots ; Blade spacers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F03—MACHINES OR ENGINES FOR LIQUIDS; WIND, SPRING, OR WEIGHT MOTORS; PRODUCING MECHANICAL POWER OR A REACTIVE PROPULSIVE THRUST, NOT OTHERWISE PROVIDED FOR
    • F03B—MACHINES OR ENGINES FOR LIQUIDS
    • F03B11/00—Parts or details not provided for in, or of interest apart from, the preceding groups, e.g. wear-protection couplings, between turbine and generator
    • F03B11/02—Casings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F03—MACHINES OR ENGINES FOR LIQUIDS; WIND, SPRING, OR WEIGHT MOTORS; PRODUCING MECHANICAL POWER OR A REACTIVE PROPULSIVE THRUST, NOT OTHERWISE PROVIDED FOR
    • F03B—MACHINES OR ENGINES FOR LIQUIDS
    • F03B13/00—Adaptations of machines or engines for special use; Combinations of machines or engines with driving or driven apparatus; Power stations or aggregates
    • F03B13/12—Adaptations of machines or engines for special use; Combinations of machines or engines with driving or driven apparatus; Power stations or aggregates characterised by using wave or tide energy
    • F03B13/14—Adaptations of machines or engines for special use; Combinations of machines or engines with driving or driven apparatus; Power stations or aggregates characterised by using wave or tide energy using wave energy
    • F03B13/141—Adaptations of machines or engines for special use; Combinations of machines or engines with driving or driven apparatus; Power stations or aggregates characterised by using wave or tide energy using wave energy with a static energy collector
    • F03B13/142—Adaptations of machines or engines for special use; Combinations of machines or engines with driving or driven apparatus; Power stations or aggregates characterised by using wave or tide energy using wave energy with a static energy collector which creates an oscillating water column
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F03—MACHINES OR ENGINES FOR LIQUIDS; WIND, SPRING, OR WEIGHT MOTORS; PRODUCING MECHANICAL POWER OR A REACTIVE PROPULSIVE THRUST, NOT OTHERWISE PROVIDED FOR
    • F03B—MACHINES OR ENGINES FOR LIQUIDS
    • F03B3/00—Machines or engines of reaction type; Parts or details peculiar thereto
    • F03B3/04—Machines or engines of reaction type; Parts or details peculiar thereto with substantially axial flow throughout rotors, e.g. propeller turbines
    • F03B3/06—Machines or engines of reaction type; Parts or details peculiar thereto with substantially axial flow throughout rotors, e.g. propeller turbines with adjustable blades, e.g. Kaplan turbines
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F03—MACHINES OR ENGINES FOR LIQUIDS; WIND, SPRING, OR WEIGHT MOTORS; PRODUCING MECHANICAL POWER OR A REACTIVE PROPULSIVE THRUST, NOT OTHERWISE PROVIDED FOR
    • F03B—MACHINES OR ENGINES FOR LIQUIDS
    • F03B3/00—Machines or engines of reaction type; Parts or details peculiar thereto
    • F03B3/12—Blades; Blade-carrying rotors
    • F03B3/128—Mounting, demounting
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05B—INDEXING SCHEME RELATING TO WIND, SPRING, WEIGHT, INERTIA OR LIKE MOTORS, TO MACHINES OR ENGINES FOR LIQUIDS COVERED BY SUBCLASSES F03B, F03D AND F03G
    • F05B2210/00—Working fluid
    • F05B2210/40—Flow geometry or direction
    • F05B2210/404—Flow geometry or direction bidirectional, i.e. in opposite, alternating directions
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02E—REDUCTION OF GREENHOUSE GAS [GHG] EMISSIONS, RELATED TO ENERGY GENERATION, TRANSMISSION OR DISTRIBUTION
    • Y02E10/00—Energy generation through renewable energy sources
    • Y02E10/20—Hydro energy
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02E—REDUCTION OF GREENHOUSE GAS [GHG] EMISSIONS, RELATED TO ENERGY GENERATION, TRANSMISSION OR DISTRIBUTION
    • Y02E10/00—Energy generation through renewable energy sources
    • Y02E10/30—Energy from the sea, e.g. using wave energy or salinity gradient

Definitions

  • the present invention relates generally to energy conversion devices. More particularly, this invention relates to turbines and primarily to unidirectional reaction turbines.
  • the invention has been developed primarily for use in an ocean wave energy extraction system employing an oscillating water column and will be described hereinafter with reference to this application. However, it will be appreciated that the invention is not limited to this particular field of use.
  • JPH10288139 A discloses an arrangement to generate power, regardless of a flow direction of fluid, by providing a plural sheets of blade members and a limiter setting the oscillating rage and revolving a rotary shaft in a fixed direction by alternately oscillating the blade members in the vertical direction by fluid flow from the upper part and lower part of the blade members.
  • fluid such as air and water from the upper part flows down within a channel of a unidirectional turbine, blade members are rotated up to a location where the blade members collide against the lower collar part of a limiter so that the free end parts may be the lower sides with a spindle as a center.
  • the blade members When fluid is blown up from the lower part, the blade members are rotated in the upper direction till the free end parts collide against an upper collar part.
  • the blade members When fluid flows continuously and alternately from the upper and lower directions, the blade members are rotated in the vertical direction, driving force is generated in the blade members by any direction and the blade members are rotated in a fixed direction with a rotary shaft as a center and power is generated by a generator.
  • DE102008007616 A1 discloses a corrugated turbine, comprising: a hub with a plurality of rotor blades with a symmetrical profile, which is configured as a drop-shaped profile, starting from a profile nose;
  • the rotor blades have a threading line whose course deviates in the rotational plane of the corrugated turbine opposite a radial jet assigned to the respective rotor blade at least in parts of the radial extent of the rotor blade.
  • the plurality of blades are arranged sequentially to form a circular array about the central axis.
  • the blades are preferably arranged in a non-overlapping sequential formation.
  • the close fitting edge-to-edge proximity between sequentially mounted blades which can be achieved with the complementary profiled leading and trailing edges advantageously results in an increased frontal surface area of each blade, and consequentially reduces the gap between blades (when viewing the rotor from the front or back - i.e. along the line of the central axis).
  • the complementary profiles provide for a substantially constant gap width along the length of the adjacent edges.
  • the gap is preferably as small as possible and only provided for mechanical working clearances. That is, the width of the gap is preferably dictated by the predetermined mechanical tolerances associated with manufacturing the blades. In certain preferred embodiments, the gap width along the length of adjacent blade edges is approximately 1mm or less.
  • This increased surface area thus enables a working fluid to pass across more blade surface which in turns improves the efficiency of the thrust arising from the lift forces generated by the working fluid flowing over the blade and accelerating through the nozzle, the thrust acting to rotate the hub and blades about the central axis.
  • each blade is mounted to the hub via a mounting means.
  • the mounting means preferably includes first mounting elements associated with the hub and second mounting elements associated with the blades, wherein each first mounting element cooperates with a respective one of the second mounting elements to securely mount the blade to the hub.
  • the mounting means preferably includes a fastening means to engage and hold the respective first and second mounting elements in fixed relation to each other.
  • the fastening means may, for example, be a fastener such as a screw or a screw and nut combination or the like.
  • each first mounting element is preferably in the form of a plurality of receiving formations in the hub for receiving the spindle or spigot of the associated blade.
  • each second mounting element is a shaft, spindle or a spigot extending from a root of the blade.
  • the blade is movable relative to the hub such that the blade can change its pitch (or angle of attack) relative to the direction of flow of the working fluid so that the hub and blades rotate in the same direction regardless of the fluid flow direction.
  • each blade moves in response to a force or pressure applied to the blade by the working fluid. That is, each blade is preferably configured to be self-rectifying such that it automatically changes its pitch in response to the prevailing characteristics of the working fluid. For example, the blades may change their pitch in response to changes in pressure and/or direction of flow of the working fluid.
  • the mounting means is configured such that all blades change their pitch at the same time and by the same degree. In other preferred embodiments, the pitch of each blade is changed independently to changes in pitch of the other blades.
  • Each blade is preferably rotatably mounted to the hub via a shaft, wherein the shaft or spindle defines an axis of rotation for that blade.
  • the shaft of each blade is mounted in a bearing arrangement in the associated receiving formation in the hub such that the blade is rotatable relative to the hub.
  • the bearing arrangement preferably includes one or more bearings and may be a stacked arrangement of two or more bearings.
  • the stacked arrangement preferably includes a stack of four angular contact thrust ball bearings.
  • Each blade preferably rotates about its associated shaft/spindle to change its pitch angle relative to the direction of flow of the working fluid so that the hub and blades rotate in one direction only about the central axis.
  • each blade is configured to be able to rotate about the spindle through a predetermined angle.
  • each blade can rotate through an angle of up to approximately ⁇ 45°, ⁇ 40°, ⁇ 35°, ⁇ 30°, ⁇ 25°, ⁇ 20°, ⁇ 15°, ⁇ 10° or ⁇ 5°.
  • each blade can rotate through an angle of up to approximately ⁇ 16°.
  • the rotatable blades can be retained in a neutral position or closed position wherein each blade is aligned around the circumference of the hub to substantially or effectively close the fluid passageway through the blades.
  • the rotatable blades preferably can also be retained at the position of their maximum forward or reverse opening positions to maintain an open passageway through the blades, the blades moving in either the forward or reverse opening direction depending on the direction of fluid flow.
  • the blades are free to rotate in order to change their pitch automatically in response to the changes to the prevailing working fluid and/or the pressure in the air chamber.
  • the changes to blade pitch are controlled by an actuator.
  • the actuator is preferably responsive to changes in the characteristics/properties of the prevailing working fluid detected by sensors arranged within the flow passage (e.g. direction of flow and/or air chamber pressure).
  • the actuator can be mechanically, electromechanically, hydraulically or pneumatically operated.
  • the actuator is configured to open the blades in a first direction (e.g. forward direction upon exhaling of air from rising wave) based on upon a first set of criteria and in a second direction (e.g. reverse direction upon inhaling of air from a receding/falling wave) based on a second set of criteria.
  • the first and second sets of criteria preferably include different parameters.
  • a control means is associated with the blades for controlling the changes in pitch.
  • the control means is preferably associated with the actuator of each blade.
  • the controls means includes a damper or spring element for providing a smooth and/or constant change in pitch.
  • the control means can vary the speed at which the blade rotates.
  • the control means can also act to limit the degree or angle to which the pitch of the blade can change.
  • the control means is in the form of a reactive mechanical spring such as, for example, a leaf spring.
  • the control means includes a torque arm.
  • the actuator and/or control means are in communication with a central controller such as, for example, a programmable logic controller (PLC).
  • PLC programmable logic controller
  • each blade is preferably curved or arcuate in shape.
  • each leading edge is convex in curvature.
  • each trailing edge is concave in curvature.
  • the curvature of the leading and trailing edges has a constant radius of curvature.
  • the radius of curvature of the leading and trailing edges varies along the length of the respective edge.
  • the radius of curvature of the leading edge is greater than the radius of curvature of the trailing edge.
  • leading and trailing edges of each blade are substantially straight. In some embodiments, the straight edges of each blade taper away from each other from the root to the tip of the blade.
  • the mounting means and shape of the blade is such that the centre-of-pressure is operatively behind the axis of rotation of the spindle of each blade so that the blade is able to rotate about its shaft in response to changes in pressure applied to the blade.
  • each blade has a generally symmetrical cross-sectional profile.
  • asymmetric profiles can be employed.
  • the cross-sectional profile is preferably in the form of an aerofoil.
  • the aerofoil has a biconvex (or convex-convexo) profile.
  • one surface of the aerofoil has a concave profile and the opposing surface is convex.
  • the aerofoil profile preferably has an enlarged rounded leading edge and tapers inwardly towards a narrower trailing edge.
  • each blade has a generally planar profile (e.g. a flat plate) with substantially parallel side faces.
  • the blades can be interchangeable with blades of a different profile so as to achieve a different operating characteristic of the turbine.
  • the trailing edge of a first blade and the leading edge of a second blade immediately following the first blade together define a nozzle.
  • the complementary shapes of the leading and trailing edges facilitate the provision of a nozzle of substantially constant width when the blades are in a neutral position or have a pitch angle of zero degrees (0°).
  • the control means preferably includes a pressure sensor for sensing the pressure in the air chamber of the oscillating water column (OWC) duct, the pressure sensor being operatively associated with the actuator and/or control means such that when a predetermined pressure is sensed the blades rotate to open the nozzles.
  • OBC oscillating water column
  • each blade is in its closed position as the oscillating water column (OWC) starts to rise (i.e. at the OWC trough) such that the air passageway is effectively closed.
  • the blades preferably open in a first direction once a predetermined pressure has been reached in the air chamber.
  • the blades return to the closed position when the wave reaches its peak.
  • a vacuum is preferably created in the air chamber.
  • the blades open in a second direction once a predetermined pressure has been reached in the air chamber.
  • the blades preferably open in the second direction once a predetermined negative pressure has been reached in the air chamber as the wave falls.
  • the tip of each blade is curved.
  • the tip of each blade is preferably convex.
  • the curvature of the tip of each blade is such that when the plurality of blades are mounted to the hub in a circular array the periphery of the array is generally in the form of a circle.
  • the turbine rotor assembly is used in a single stage turbine.
  • the turbine is preferably a unidirectional reaction turbine.
  • the turbine rotor assembly could readily be adapted for use in multi-stage turbines having two or more rotors.
  • the turbine rotor assembly is advantageously suited for use in extracting energy from an oscillating working fluid. More particularly, the turbine rotor assembly is suitable for use in an oscillating water column (OWC) energy extraction system having an OWC duct.
  • the rotor assembly is preferably mounted in the OWC duct of the energy extraction system such that an air chamber is defined within the duct between the surface of the water in the duct and the hub and blades.
  • the rotor assembly is preferably adapted for rotation in a single direction, independent of the direction of fluid flow.
  • the rotor is arranged to be substantially normal to the direction of fluid flow with the axis of rotation substantially parallel to the fluid direction.
  • the plurality of blades of the rotor assembly is preferably configured such that the rotor rotates in a predetermined direction.
  • the rotor assembly is arranged substantially normal to the flow direction of the working fluid such that it rotates about the longitudinal axis of the housing.
  • the rotor assembly is arranged to rotate in a direction substantially parallel to the fluid flow direction.
  • the turbine rotor assembly is rotatably arranged within a flow passage of a housing.
  • the housing is preferably configured to direct the flowing working fluid towards the blades of the rotor assembly.
  • the housing is configured to have tapered or curved surfaces associated with the flow passage for directing the working fluid towards the blades.
  • the housing is preferably longitudinal and extends along a longitudinal axis.
  • the housing has a generally cylindrical body.
  • the turbine rotor assembly is arranged substantially coaxially with the longitudinal axis of the housing.
  • the housing is arranged such that its longitudinal axis is arranged substantially parallel to the direction of flow of the oscillating working fluid. In other embodiments, the housing is arranged such that its longitudinal axis is arranged substantially normal to the direction of flow of the oscillating working fluid.
  • the housing could be arranged such that the longitudinal axis is substantially vertical. In other preferred forms, the housing could be arranged such that the longitudinal axis is substantially horizontal. It will be appreciated by those skilled in the art that the housing is not limited to those orientations described above, but could be arranged in any other suitable orientation, relative to the direction of flow of the working fluid, to suit a particular application.
  • guide means is provided upstream of the rotor for directing the working fluid towards the blades of the rotor.
  • the guide means includes first and second guides arranged on opposite sides of the rotor to direct the working fluid onto the blades at a desired angle.
  • the guide means includes one or more guide vanes arranged upstream of the rotor for directing the working fluid towards the blades of the rotor.
  • the guide vanes are preferably arranged in a polar or circular array in proximity to the blades.
  • the guide vanes may be associated with a stator or otherwise arranged within the housing.
  • the guide means includes a nose cone extending from the hub.
  • guide vanes are not limited to a particular form and therefore could be any suitable shape, including curved and planar shapes, for deviating the working fluid towards the rotor blades.
  • the oscillating working fluid is preferably an oscillating airflow.
  • the turbine rotor is configured for rotation by an airflow generated from an oscillating water column of an ocean wave energy extraction system, the oscillating water column (and thus the airflow) oscillating in response to the rise or fall of passing ocean waves.
  • the oscillating working fluid is not limited to an oscillating airflow, and in particular, is not limited to an oscillating airflow produced from an oscillating water column.
  • the turbine rotor assembly can be adapted for use with a unidirectional working fluid.
  • the blades can be arranged in an overlapping formation wherein the leading and trailing edges of sequential blades overlap each other.
  • the rotor has a drive shaft coupled at its proximal end to the hub such that rotation of the hub causes a corresponding rotation of the drive shaft such that its distal end can be used to engage and drive an electric generator.
  • the hub preferably has a mass which is sufficient for it to act as a flywheel to provide a substantially constant angular velocity, in use.
  • a turbine for extracting energy from an oscillating working fluid including:
  • an ocean wave energy extraction system including:
  • the invention provides a turbine rotor assembly 1 for extracting energy from an oscillating working fluid in the form of an oscillating airflow.
  • the turbine rotor assembly 1 has been developed specifically for use in an ocean wave energy extraction system ( Figure 12 ) of the type having an oscillating water column.
  • the oscillating water column is configured to produce the oscillating airflow in response to the rise and fall of passing ocean waves.
  • the OWC rises in response to a passing wave crest the OWC rises to produce an exhaust airflow.
  • the OWC falls to produce an intake airflow.
  • the turbine rotor assembly 1 includes a hub 2 which is rotatable about its central axis 3.
  • a plurality of blades 4 are mounted to the hub 2 about the central axis.
  • the blades are arranged in a non-overlapping, sequential formation so as to form a circular array about the central axis 3 of the hub 2.
  • the hub has a series of first mounting elements in the form of radial bores 5 circumferentially arranged about the periphery of the hub 2.
  • Each blade 4 has a second mounting element in the form of a spindle 6 which is received in an associated bore 5 of the hub 2.
  • Each spindle 6 includes a bearing element 7 which enables the associated blade 4 to be rotatable relative to the hub 2, about an axis of rotation defined by the spindle 6.
  • Each blade 4 is configured to be able to rotate about its spindle 6 through a predetermined angle. In the illustrated embodiment, each blade 4 can rotate through an angle, for example, approximately ⁇ 24°. In Figures 1 to 4 , the blades 4 have rotated to a position suitable for an exhaust airflow (flowing left-to-right in Figure 3 ).
  • Each blade 4 moves in response to a force applied to the blade by the prevailing airflow fluid, the force arising from a pressure difference across the blades.
  • the ability of the blades to change their pitch angle provides the rotor 1 with a self-rectifying characteristic.
  • the blades 4 can be rotated to suit either an intake or an exhaust airflow and maintain rotation of the hub 2 in a single direction about its central axis.
  • a control means in the form of a reactive mechanical spring such as a leaf spring 8 is associated with each blade 4 for controlling the changes to the pitch angle.
  • the leaf spring 8 acts to provide a smooth and/or constant change in pitch.
  • the leaf spring limits the degree to which the pitch of the blade can change.
  • each blade 4 has a leading edge 11 and a trailing edge 12.
  • the leading and trailing edges (11, 12) are advantageously configured to have complementary profiles to each other such that the blades 4 can be mounted to the hub 2 in close fitting edge-to-edge proximity to each other.
  • the close fitting edge-to-edge proximity between sequential blades which can be achieved with the complementary profiled leading and trailing edges, advantageously results in an increased frontal surface area of each blade, and consequentially reduces the gap between blades (when viewing the rotor from the front or back - i.e. along the line of the central axis).
  • the complementary profiles provide for a substantially constant gap width along the length of the adjacent edges (11, 12).
  • the gap between the blades is merely a clearly gap and minimised to the available manufacturing tolerances.
  • the total gap area is negligible and is sufficient to effectively close the passageway and almost totally obstruct the flow of air through the blades.
  • the solidity ratio i.e. the ratio of the total combined blade area to the swept area of the blades
  • the closed blades inhibit the intake of air into the air chamber and thus allow the pressure in the chamber to drop.
  • the ability to hold the blades closed until a predetermined pressure is reached advantageously increases the magnification of the wave height in the OWC duct to thereby improve the efficiency of the turbine. It has been numerically modelled that an improvement in the total energy extraction can be achieved by holding the blades closed.
  • the increased surface area enables the airflow to pass across more blade surface which in turn provides additional lift and thrust forces for rotating the hub and thus improves the efficiency of the rotor 1, as described in further detail below.
  • This improved efficiency arises from an improved pressure profile across each blade as shown in Figure 9 .
  • the substantially constant width of the gap defines a nozzle which, at least in preferred forms, operates to increase the velocity of the prevailing airflow, further increasing the lift and thrust forces applied to the blades.
  • the mounting means and shape of the blade is such that the centre-of-pressure (COP) is operatively behind the axis of rotation of the spindle of each blade. That is, the leading and trailing edges curve away from the spindle to place the centre-of-pressure behind the axis of rotation to enable the blade to rotate about the axis of rotation.
  • COP centre-of-pressure
  • each blade preferably has a symmetrical cross-sectional profile.
  • the turbine rotor assembly 1 is rotatably arranged within a flow passage of a cylindrical housing 9.
  • the housing 9 is preferably configured to have curved inlet opening for directing the airflow towards the blades of the rotor.
  • a nose cone 10 extending from the hub 2 is provided.
  • the hub 2 of the rotor 1 is preferably coupled to a drive shaft which is engaged to an electric generator (not shown). Rotation of the hub 2 causes a corresponding rotation of the drive shaft to drive the electric generator.
  • the arrangement of the blades on the rotor assembly is such that in the neutral or non-actuated position, the fluid flow passage through the housing is almost entirely blocked by the blades (albeit for the small clearance gaps between sequential blades and between the tips of the blades and the housing). Such a blockage creates a full differential pressure across the blades between the upstream and the downstream flow directions.
  • Computational fluid dynamic (CFD) analysis has shown that a very thin section blade yields excellent results and an aerofoil section shape is not critical.
  • This blockage of fluid flow establishes a pressure difference across the blades on the upstream and downstream sides of the blades.
  • the pressure difference creates a force normal to the surface of the blades with a resultant force comprising a component in the axial rotation direction of the rotor and a component in the direction of rotation of the rotor, this component being the torque that produces the power from the turbine.
  • upstream and downstream are used in a relative sense, dependent upon the direction of flow of the oscillating airflow.
  • the working fluid is allowed to pass between the nozzles created between the leading and trailing edges of the sequentially arranged blades.
  • the nozzles are created by a geometric rotation of the blades about an axis of rotation orthogonal, but not necessarily perpendicular to, the axis of rotation of the central axis of the hub.
  • the nozzles allow the working fluid to flow through the array of blades in a preferred manner and rate such that the pressure differential across the upstream and downstream sides of the blade array is not substantially reduced compared to the pressure created when the blades are in their neutral position. That is, the pressure difference across the blades from the upstream to the downstream sides of the blades is advantageously substantially maintained when the nozzles are created by actuation of the blades from their neutral position.
  • each nozzle is by rotation of the entire blade about an axis orthogonal to the central axis of the hub.
  • the nozzles may be formed via the structural deformation of the blade. Such shape deformation may be via the applied fluid pressure on the blade surface contributing to the deformation or via other electromechanical induced control methods.
  • the configuration and profile of the nozzles can produce a secondary benefit to the induced power producing thrust of the blades.
  • the leading and trailing edges are preferably shaped to define a nozzle profile with a smooth area reducing section to cause the flowing fluid to accelerate through the nozzle, thereby exchanging pressure energy for kinetic energy.
  • the consequence of which is a further reduction in pressure over the leading edge and forward section of the blades on the downstream side.
  • This pressure reduction results in a normal force with a component in the axial and the rotational directions.
  • the rotational direction force is converted to torque about the central axis, whereby this extra contribution may further enhance the magnitude of the rotational force vector.
  • the blade pitch angle and the corresponding pressure in the air chamber can be seen for a complete wave cycle in Figure 11 . It can be clearly seen from Figure 11 that the blades are held closed when the blade is rising from its trough until a predetermined pressure is reached in the chamber. The blades are also held closed from the time the peak of the wave is reached until it falls and creates a second (negative) predetermined pressure in the chamber.
  • a mechanical spring system containing a spring pretension force is used.
  • a hydraulic piston with a preload fluid pressure that is defined by the pressure in an accumulator or mechanic spring piston accumulator can be used.
  • a magnetic actuator system with a preset holding force could also be used.
  • the closing of the blades includes a time dependent damping system such that the closing rate of the blades is reduced and blade closing rate becomes independent of the pressure in the OWC (i.e. the damping system acts against the spring pretension force).
  • This system allows all of the air in the OWC chamber to escape at the end of the wave stroke. This allows for a greater internal wave height amplitude at the beginning of the next stroke as well as allowing more air to be entrained in the chamber before the up stroke and less air to be entrained in the chamber before the commencement of the down stroke.
  • the preset opening pressure is adjusted such that the preset opening pressure is a function of the rotational speed (rpm) of the turbine.
  • This enhancement allows the turbine to operate in its optimal efficiency range as well as allowing the turbines rpm to more closely match the available wave energy states, specifically the height of the incoming waves.
  • the inhale and exhale cycles of the turbine blade pitch control can be independent from each other, as per the mechanisms described above.
  • the ability to control the blades such that they are held closed until a predetermined pressure is reached in the air chamber advantageously magnifies the amplification of the OWC and thereby increases the amount of pneumatic power extracted and improves the efficiency of the turbine.
  • the present invention provides a turbine rotor assembly of increased efficiency.
  • the turbine rotor assembly advantageously enables increased amounts of energy to be extracted from an oscillating or bidirectional working fluid.
  • the turbine rotor assembly has blades which advantageously provide an increase frontal area of the turbine blades which constricts the fluid flow passage to create a greater pressure differential across the blades, resulting in increases in the lift and thrust forces being applied to the blades.
  • the close fitting edge-to-edge proximity of the blades also advantageously provides for nozzles which can increase the velocity of the airflow, again increasing the pressure difference across the blade with a resultant increase in thrust.
  • the turbine rotor assembly is particularly suited for use in an ocean wave energy extraction system, wherein the working fluid is an oscillating airflow generated by an oscillating water column of the ocean wave energy extraction system, the oscillating water column (and thus the airflow) oscillating in response to the rise of fall of passing ocean waves.
  • the invention in its preferred embodiments, represents a practical and commercially significant improvement over the prior art.

Claims (15)

  1. Ensemble rotor de turbine (1) pour extraire de l'énergie d'un fluide de travail oscillant, l'ensemble rotor de turbine (1) comprenant :
    un moyeu (2) apte à tourner autour d'un axe central (3) ;
    une pluralité d'aubes (4) aptes à être montées sur le moyeu (2) autour de l'axe central (3) ;
    chaque aube ayant un bord d'attaque et un bord de fuite ; le bord d'attaque et le bord de fuite étant configurés pour être complémentaire en profil l'un de l'autre de telle sorte que les aubes peuvent être montées à proximité étroite bord-à-bord les unes par rapport aux autres ;
    chaque aube (4) étant mobile par rapport au moyeu (2) de telle sorte que chaque aube (4) peut changer son pas par rapport à la direction d'écoulement du fluide de travail ; et
    la pluralité d'aubes (4) étant agencées pour être commandées de telle sorte qu'en utilisation les aubes (4) sont maintenues dans une position fermée pour bloquer un passage de fluide à travers les aubes (4) jusqu'à ce qu'une pression prédéterminée du fluide de travail soit atteinte.
  2. Ensemble rotor de turbine (1) selon la revendication 1, dans lequel la pluralité d'aubes (4) sont disposées séquentiellement pour former un réseau circulaire autour de l'axe central,
    facultativement, les aubes (4) sont disposées en formation séquentielle non-chevauchante.
  3. Ensemble rotor de turbine (1) selon l'une quelconque des revendications précédentes, dans lequel chaque aube (4) est montée sur le moyeu par l'intermédiaire d'un moyen de montage, ledit moyen de montage comprenant une pluralité de formations de réception (5) dans le moyeu (2) et un arbre (6) s'étendant à partir d'une emplanture de chaque aube (4), chaque arbre (6) étant apte à être reçu dans l'une respective des formations de réception (5).
  4. Ensemble rotor de turbine (1) selon la revendication 3, dans lequel chaque aube (4) se déplace en réponse à une force appliquée à l'aube (4) par le fluide de travail,
    facultativement, le moyen de montage est configuré de telle sorte que toutes les aubes (4) changent leur pas en même temps et du même degré.
  5. Ensemble rotor de turbine (1) selon la revendication 4, dans lequel chaque aube (4) est apte à tourner autour de son arbre associé (6) pour changer son angle de pas par rapport à la direction d'écoulement du fluide de travail de telle sorte que le moyeu (2) et les aubes (4) tournent dans une seule direction autour de l'axe central (3), indépendamment de la direction d'écoulement de fluide,
    facultativement, chaque aube (4) est configurée pour être apte à tourner autour de l'arbre (6) d'un angle prédéterminé.
  6. Ensemble rotor de turbine (1) selon l'une quelconque des revendications précédentes, dans lequel un mouvement des aubes (4) est commandé par un actionneur, et ledit actionneur est sensible aux changements dans les propriétés du fluide de travail prédominant à l'intérieur du passage d'écoulement,
    facultativement, l'actionneur est configuré pour ouvrir les aubes (4) dans une première direction sur la base d'un premier ensemble de critères et dans une seconde direction sur la base d'un second ensemble de critères.
  7. Ensemble rotor de turbine (1) selon la revendication 6, dans lequel un moyen de commande est en communication avec l'actionneur pour commander un mouvement des aubes (4),
    facultativement, le moyen de commande comprend un amortisseur pour assurer un changement de pas sans à-coups et/ou constant, ledit amortisseur étant agencé pour commander la vitesse à laquelle la aube (4) tourne.
  8. Ensemble rotor de turbine (1) selon l'une quelconque des revendications précédentes, dans lequel chaque aube est apte à être montée sur le moyeu de telle sorte qu'un centre de pression de chaque aube se trouve fonctionnement derrière un axe de rotation de l'aube associée.
  9. Ensemble rotor de turbine (1) selon l'une quelconque des revendications précédentes, dans lequel chaque aube (4) a un profil de section transversale généralement symétrique.
  10. Ensemble rotor de turbine (1) selon l'une quelconque des revendications précédentes, dans lequel le profil de section transversale de chaque aube (4) est un profil aérodynamique,
    facultativement, le profil aérodynamique a un bord d'attaque arrondi agrandi (11) et s'effile vers l'intérieur vers un bord de fuite plus étroit (12).
  11. Ensemble rotor de turbine (1) selon l'une quelconque des revendications précédentes, dans lequel le bord de fuite (12) d'une première aube (4) et le bord d'attaque (11) d'une deuxième aube (4) suivant immédiatement la première aube (4) définissent ensemble une buse.
  12. Ensemble rotor de turbine (1) selon la revendication 7, comprenant un capteur de pression pour détecter la pression dans une chambre à air d'une conduite de colonne d'eau en oscillation, dans lequel le moyeu (2) et les aubes (4) sont disposés, le capteur de pression étant associé fonctionnellement à l'actionneur et/ou au moyen de commande de telle sorte que, lorsqu'une pression prédéterminée est détectée, les aubes (4) tournent pour ouvrir les buses.
  13. Ensemble rotor de turbine (1) selon l'une quelconque des revendications précédentes, dans lequel un arbre d'entraînement est accouplé au moyeu (2) au niveau de son extrémité proximale et à une génératrice électrique au niveau de son extrémité distale.
  14. Ensemble rotor de turbine (1) selon l'une quelconque des revendications précédentes, dans lequel le fluide de travail est généré par une vague océanique, et les aubes (4) sont maintenues dans la position fermée lorsqu'une vague s'élève à partir de son creux jusqu'à ce que la pression prédéterminée soit atteinte.
  15. Ensemble rotor de turbine (1) selon l'une quelconque des revendications précédentes, dans lequel le fluide de travail est généré par une vague océanique, et les aubes (4) sont maintenues dans la position fermée lorsque la vague tombe à partir de son sommet jusqu'à ce qu'une seconde pression prédéterminée soit atteinte.
EP11833628.8A 2010-10-22 2011-10-21 Ensemble rotor de turbine Active EP2630366B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
AU2010904731A AU2010904731A0 (en) 2010-10-22 Turbine rotor assembly
PCT/AU2011/001333 WO2012051656A1 (fr) 2010-10-22 2011-10-21 Ensemble rotor de turbine

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EP2630366A1 EP2630366A1 (fr) 2013-08-28
EP2630366A4 EP2630366A4 (fr) 2017-01-18
EP2630366B1 true EP2630366B1 (fr) 2018-07-11

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EP11833628.8A Active EP2630366B1 (fr) 2010-10-22 2011-10-21 Ensemble rotor de turbine

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US (2) US9279333B2 (fr)
EP (1) EP2630366B1 (fr)
JP (1) JP6091418B2 (fr)
CN (1) CN103348129B (fr)
AU (1) AU2011318238B2 (fr)
CA (1) CA2815245C (fr)
DK (1) DK2630366T3 (fr)
ES (1) ES2690468T3 (fr)
NZ (1) NZ609330A (fr)
PT (1) PT2630366T (fr)
WO (1) WO2012051656A1 (fr)

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Also Published As

Publication number Publication date
PT2630366T (pt) 2018-11-06
JP2013543559A (ja) 2013-12-05
US20160186713A1 (en) 2016-06-30
AU2011318238B2 (en) 2016-06-02
CA2815245C (fr) 2019-04-16
EP2630366A1 (fr) 2013-08-28
US20130255246A1 (en) 2013-10-03
EP2630366A4 (fr) 2017-01-18
CN103348129B (zh) 2016-10-12
JP6091418B2 (ja) 2017-03-08
NZ609330A (en) 2015-04-24
DK2630366T3 (en) 2018-10-29
US9279333B2 (en) 2016-03-08
CA2815245A1 (fr) 2012-04-26
ES2690468T3 (es) 2018-11-21
AU2011318238A1 (en) 2013-05-02
AU2011318238A8 (en) 2016-05-26
WO2012051656A1 (fr) 2012-04-26
CN103348129A (zh) 2013-10-09

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